Intake and exhaust valve system for an internal combustion engine

ABSTRACT

In an internal combustion engine, first and second rotating members, one for the intake valve and one for the exhaust valve rotate next to the outside of an engine cylinder on opposite sides thereof when driven by a drive gear attached to the end of the engine&#39;s crankshaft. Each rotating member may include a ring gear having a valve port or aperture near its perimeter that cyclically aligns with a corresponding valve port formed through the cylinder wall near the top of the cylinder. A method of controlling valve timing comprises the steps of causing the rotating member containing the second valve port to periodically align in synchronism with the first port to control the passage of an air/fuel mixture and exhaust gases through the combustion cycles of the engine.

1. CROSS-REFERENCE TO RELATED APPLICATION

The present application claims priority to U.S. Provisional PatentApplication Ser. No. 62/697,183, filed Jul. 12, 2018, entitled “ValveSystem for an internal Combustion Engine”, by the same inventor.

2. FIELD OF THE INVENTION

The present application relates generally to internal combustion enginesand more particularly to apparatus and methods for control of the intakeand exhaust valve systems of internal combustion engines.

BACKGROUND OF THE INVENTION

An internal combustion engine admits a combustible mixture, usually airand a fuel such as gasoline or a blend of gasoline and ethanol into aclosed chamber to be ignited by an energetic impulse such as an electricspark. In the case of diesel engines, ignition occurs when the incomingair is heated by compression and mixed with fuel injected into thecombustion chamber. The expansion of the ignited fuel forces movement ofa piston or other component coupled through reciprocating or rotarymotion to cause cyclic rotation of an output shaft called a crankshaft.The rotating crankshaft may be coupled through a transmission ordriveshaft to provide motive force to a machine such as a vehicle orappliance. The output of the engine may be controlled by adjusting theair/fuel mixture inlet into the combustion chamber.

In the design of internal combustion engines, there are three kinds oftiming functions that must be satisfied: (1) timing the valves thatcontrol the passage of air into and exhaust gases out of the combustionchamber; (2) timing the injection of fuel into the air/fuel mixture orinto the combustion chamber, and (3) timing the spark or other energeticimpulse that provides ignition of the air/fuel mixture in the combustionchamber.

The conventional types of apparatus for the intake and exhaust valvesystems for internal combustion engines are well known, includingcamshaft-controlled reciprocating poppet-valve mechanisms wherein thespring-loaded valves activated by a camshaft embedded in the engineblock and driven by a gear attached to the crankshaft that meshes with agear attached to the camshaft. Alternatively, the camshaft may belocated outside the engine block and driven by a toothed belt and pulleyconfiguration synchronized with the crankshaft. The camshaft hasprecisely-shaped lobes that convert the rotary motion of the camshaft tolinear motion through a mechanical system of lifters, push rods, androcker arms mounted on the cylinder head to the valve stems (a so-called“valve train”) that reciprocate in valve guide passages through thecylinder head. The poppet valves on the opposite end of the valve stemsare held closed under spring tension until the camshaft lobe raises thelifter in a motion imparted through the valve train to open the valve.Alternatively, the camshaft may be mounted on the cylinder head directlyabove the valves where the lobes on the camshaft can directly contactthe valve stem or an intervening valve lifter. The camshaft may bedriven by a chain or belt coupled to a sprocket or pulley attached tothe crankshaft. These types of poppet valve trains are complex, havemany precision moving parts of relatively high mass subject toreciprocating motion and wear, and require substantial maintenance.

Other valve systems such as rotary valves where the valve member isrotated through a mechanism to move a valve passage into alignment withinlet or outlet passages are conceptually among the simplest valvesystems, finding uses in applications ranging from water faucets tobrass horn instruments, and even to some types of engines. While suchvalve systems can be simpler than the inefficient and complexreciprocating mechanisms for operating intake and exhaust valves,conventional designs still involve mechanisms subject to a variety ofproblems. What is needed is a conceptually simple mechanism foroperating the intake and exhaust valves of an internal combustion enginethat is efficient, practical, and cost effective.

SUMMARY OF THE INVENTION

A valve system for an internal combustion piston engine having acrankshaft rotatably mounted in a crankcase portion of an engine block,and an engine cylinder formed within the engine block and open at alower end thereof into the crankcase, comprising a first port disposedthrough a side wall of the engine cylinder into an upper portion of theengine cylinder; and a second port disposed through a rotating portmember along one radius of the rotating port member; wherein therotating port member is disposed to rotate alongside the side wall ofthe engine cylinder such that the second port and the first port are ina communicating alignment keyed to revolution of the crankshaft. Thesystem preferably includes at least one rotating drive member forcoupling the rotation of the crankshaft to rotation of the rotating portmember to control timing of the communicating alignment of the first andsecond ports.

In one aspect, the at least one rotating drive member comprises a ringgear attached to the crankshaft and aligned with the axis of thecrankshaft and having a plurality of gear teeth around the ring gearthat mesh with corresponding teeth formed around the rotating portmember. In this aspect the number of gear teeth around the rotatingdrive member equals half the number of gear teeth disposed around therotating port member such that the rotating drive member rotates twocomplete revolutions for each revolution of the rotating port member forfour cycle operation. In an alternate aspect, the number of gear teetharound the rotating drive member equals the number of gear teethdisposed around the rotating port member such that the rotating drivemember rotates one complete revolution for each revolution of therotating port member for two cycle operation.

In second embodiment, the rotating port member comprises a rotating dischaving a plurality of gear teeth disposed around the perimeter of thedisc, and a cylindrically-formed ring having first and second paralleledges and coaxially attached at the first edge thereof to a side of therotating disc facing the engine cylinder, wherein the second port isformed in the ring between the first and second parallel edges. In thisembodiment, the first port comprises a first aperture disposed through aportion of a top side of the engine cylinder disposed opposite the openend of the engine cylinder, a second aperture is disposed in thecylindrically-formed ring, the second aperture having a shape and sizethat corresponds with the first port when the first and second ports arein communicating alignment; and the top side of the engine cylinder is acylinder head.

In one aspect of the second embodiment, the at least one rotating drivemember comprises a ring gear attached to the crankshaft aligned with theaxis of the crankshaft and having a plurality of gear teeth around thering gear that mesh with corresponding teeth formed around the rotatingport member. In this aspect the number of gear teeth around the rotatingdrive member equals half the number of gear teeth disposed around therotating port member such that the at least one rotating drive memberrotates two complete revolutions for each revolution of the rotatingport member for four cycle operation. In an alternate aspect the numberof gear teeth around the rotating drive member equals the number of gearteeth disposed around the rotating port member such that the at leastone rotating drive member rotates one complete revolution for eachrevolution of the rotating port member for two cycle operation.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1A through 1J illustrate isometric views depicting several membersof the family of embodiments of the present invention;

FIG. 2 illustrates an isometric view of a first embodiment of thepresent invention;

FIG. 3 illustrates an isometric view of a second embodiment of thepresent invention;

FIG. 4 illustrates an isometric view of a third embodiment of thepresent invention;

FIG. 5 illustrates an isometric view of a fourth embodiment of thepresent invention;

FIG. 6 illustrates a schematic cross section of a conceptual embodimentof the present invention;

FIG. 7 illustrates a side view of an engine cylinder as formed in theembodiment of FIG. 2;

FIG. 8 illustrates four views, FIGS. 8A, 8B, 8C, and 8D, of amulti-stage valve system for use in the embodiment of FIG. 2;

FIG. 9 illustrates a top-down view of a cross section of an enginecylinder according to the embodiment of FIG. 2 that includes themulti-stage throttle valve system depicted in FIG. 8 in aclosed-throttle state;

FIG. 10 illustrates a top-down view of a cross section of an enginecylinder according to the embodiment of FIG. 2 that includes themulti-stage throttle valve system depicted in FIG. 8 in an open-throttlestate;

FIG. 11 illustrates an isometric view of a cylinder bead portion of theembodiment of FIG. 4;

FIG. 12 illustrates a timing gear set for use with the embodiment ofFIG. 11;

FIG. 13A through 13J illustrate a family of symbolic cross sectiondrawings that correspond to the members of the family of embodimentsdepicted in FIGS. 1A through 1J;

FIGS. 14A and 14B illustrate a method for timing the operation of intakeand exhaust valves of an internal combustion engine according to thepresent invention; and

FIG. 15 illustrates an alternate structure for sealing the intake andexhaust ports according to the present invention.

DETAILED DESCRIPTION OF THE INVENTION

In an advance in the state of the art, the disclosed inventioneliminates the conventional camshaft and reciprocating valve train tocontrol the timing of the intake and exhaust cycles of an internalcombustion engine (“ICE”) such as the well-known two or four cycle,spark ignition engines. The system includes intake and exhaust portvalves for admitting the air/fuel mixture into the cylinder andexhausting the burned gases of combustion from the cylinder. Timing orsynchronizing the opening and closing of these valves is one of thethree kinds of timing functions that must be satisfied in an internalcombustion engine: timing the valves, the injection of fuel, and thespark or other energetic impulse that provides ignition of the air fuelmixture.

In principle, the valves are configured as ports or apertures formed ina rotating member disposed adjacent fixed intake and exhaust ports intoor out of the engine cylinder. The concept is illustrated in theattached concept figures for a single cylinder, four cycle engine, butis adaptable to two cycle engines and other operating cycles. Thedrawings include views of several alternative embodiments, depending onthe location of the fixed ports into the cylinder and the configurationof the rotating ports for their cyclical, synchronized alignment withthe fixed ports. The illustrated specimens depict variations of therotating valve port (“RVP”) concept embodied in the disclosed invention.In some examples the RVP periodically aligns with a fixed valve portformed in the side wall of the engine cylinder. In other examples, theRVP periodically aligns with a fixed valve port formed in the top sideor ceiling of the engine cylinder, typically called the cylinder head.In both examples, the valve ports open into a combustion chamberdisposed in the upper portion of the engine cylinder. Each enginecylinder includes an intake valve port and an exhaust valve port thatcommunicates with the combustion chamber of the engine cylinder. Inletor outlet passages coupled with the intake or exhaust ports respectivelymay be parts of a manifold as in a typical internal combustion engine.

In the following descriptions of the drawings, several terms needdefining. The engine cylinder in the embodiments illustrated herein,through which the piston reciprocates, includes a combustion chamber atthe end opposite the crankcase. The combustion chamber may reside withinthe upper portion of the cylinder and include a portion of its volume ina cylinder head that forms the top side of the cylinder. The enginecylinder may be defined by a cylinder wall having an inside surface andan outside surface, referred to herein as a side wall. The rotatingvalve port structure, may be a disc or ring gear, or a ring gear havinga cylindrical ring or a cylindrical extension of one side of the ringgear. In some embodiments, the cylindrical ring may have a relativelyshort axial length; in other embodiments, the cylindrical ring may beelongated to have a more substantial length so that it resembles atubular component.

The rotating valve port structure (aka rotating port member) may also beunderstood as a driven gear that meshes with a drive gear attached tothe crankshaft and shares its axis with the crankshaft. Further, therotating valve port may be supported by a bearing disposed on an axlesuch as a shoulder bolt secured to the engine block. Details of thebearing and axle are omitted from the drawings to provide clarity of theessential features of the rotating valve port concept. Bearings andaxles are mechanical elements that are well-understood by personsskilled in the art. In one example, a bushing or bearing disposed on ashoulder bolt as an axle may be used to support the rotating valve port.Alternatively, a semi-circular cradle (see, e.g., page 11) may supportthe rotating valve port in a cradle like structure. Bearing surfaces mayinclude babbit-type bearing inserts, ball bearings, bushings, or simplybearing surfaces that are hardened or coated with wear-resistant ceramiccompounds. Other surfaces in contact with moving parts may also behardened or coated with wear-resistant ceramic compounds.

The drawings are organized as follows. FIG. 1 depicts isometric views ofeach of ten exemplary embodiments of the rotating valve port concept,FIGS. 2 through 5 depict enlarged examples of four of the embodimentsshown in FIG. 1 to illustrate the relationships of essential parts ofthe engines. The four embodiments of FIGS. 2 through 5 illustrate twobasic configurations of the invention: (A) placing the rotating valveport along the outer side of the engine cylinder (FIGS. 2 and 5), and(B) placing the rotating valve port over the top side of the enginecylinder to connect the inlet or exhaust passages through the cylinderhead (FIGS. 3 and 4). FIG. 6 is a schematic cross section view of a typeA configuration to describe the structure and operation of theside-disposed rotating valve port embodiments. FIG. 7 illustrates oneembodiment of a sealing structure around a valve port in a type Aconfiguration. FIGS. 8A through 8D, 9 and 10 depict several states of asecondary Multi-Stage valve for use with embodiments of the rotatingvalve concept to vary the cross section area of a port. FIGS. 11-12 areschematic depictions of a type B configuration—the top-side-disposedrotating valve port embodiments. FIG. 13 illustrates symbolicrepresentations of the ten embodiments shown in FIG. 1. FIG. 14 providesa flow chart of a method of timing the operation of the intake andexhaust valves. FIG. 15 depicts one embodiment of a sealing structurethat confines leakage gases to the immediate region around the joint inthe port passages between the rotating and fixed portions of the portstructure. Further, in regard to FIGS. 1 through 5, the engine cylinder,combustion chamber, and manifolds are omitted from the isometric viewsto more clearly show the relationship of the rotating valve ports withthe piston, as will become clear in the following to description. Theview in FIG. 6 includes the engine cylinder head and the combustionchamber.

FIGS. 1A through 1J illustrate isometric views depicting several membersof the family of embodiments of the present invention. The illustrationsinclude a crankshaft and piston assembly, the rotating gear elements,and an outside of an engine block, but omit the engine cylinder,cylinder head and manifolds to more clearly depict the essentialcomponents of the structure. Ten configurations are shown, representingtwo orientations of a rotating valve port disposed next to the outerside of an engine cylinder (type A) or next to the top or cylinder headof the engine cylinder (type B). The concepts of the invention areillustrated for a single cylinder, four cycle engine but are adaptableto multiple cylinder engines formed for four or two cycle operation, andto engines designed to operate on gasoline, diesel and other types offuels. Each of the embodiments is labeled with an identifier of the formRVP-1, RVP-2, . . . RVP-10, where RVP denotes a “rotating valve port”configuration. Examples RVP-1, 4, 5, 8 and 10 depict type A embodimentsof the port configuration and RVP-2, 3, 6, 7 and 9 depict type Bembodiments of the port configuration.

The rotating valve port is formed in a rotating gear or a cylindricalextension of one side of the rotating gear. The rotating gear (aka arotating port or driven gear) is driven by a drive gear disposed on arotating crankshaft. In some implementations an idler gear may bedisposed between the drive gear and the rotating valve port gear. Inembodiments having the rotating port formed in a cylindrical extensionof one side of the rotating gear, the cylindrical extension isconfigured as a cylindrically-formed ring having first and secondparallel edges that define the ends of the cylindrical extension. Insome embodiments the cylindrical extension appears as a “short”cylinder; in other embodiments, the cylindrical extension appears as alonger cylinder. In either case, the cylindrical extension may becoaxially attached at the first edge thereof to a side of the rotatingdisc facing the engine cylinder, such that the second port is formed inthe ring between the first and second parallel edges as shown in FIG. 1for the RVP-2 and RVP-6 and RVP-7 configurations.

In general, the rotating ports, and the fixed ports formed in the outerwall of the engine cylinder, may be formed as an aperture elongated inthe radial direction of rotation of the rotating port valve. A fixedport in the outer side wall of the engine cylinder may be oriented alonga perimeter of the engine cylinder surface, and termed as a simplerectangular shape varied from square to elongated, or it may be formedto be round or oval. Other shapes and orientation are possible and notlimited to these alternatives. A rotating port may likewise vary inshape and orientation in the rotating valve disc. As the rotating valvepasses the fixed port in the wall of the engine cylinder, the valveopens as the rotating valve port passes over the fixed port, firstincreasing in open area cross section, reaching a maximum aperture, thendecreasing in open area cross section. The shape of the valve ports maybe varied to adjust the particular valve opening profile to suit thecharacteristics of the engine design. For example, the shape may betailored to vary the speeds of the increase and decrease in the portapertures.

RVP-1 (reference number 10) in FIG. 1A shows a first and a secondrotating gear, each disposed on opposite sides of a piston. Eachrotating gear includes a port formed through the body of the gear nearthe perimeter of the gear. As the gear rotates, the port in that gearbecomes periodically aligned with a fixed port in an upper side wall ofthe engine cylinder. This embodiment may be considered the original andmost basic implementation, RVP-2 (40) in FIG. 1B is similar but isdifferent in one key aspect: the rotating ports are formed in a short,cylindrical extension of the side of each rotating gear facing thepiston. The cylindrical extension may be formed as a thin ring in whichthe axial length of the ring body's cross section is substantiallygreater than the radial thickness of the ring body's cross section. Asthe RVP gear rotates, the cylindrical extension or ring revolves in arelief formed in the engine block and cylinder head (the relief is notshown in FIG. 1B) such that the rotating port becomes periodicallyaligned over a fixed port in the cylinder head that forms the top end ofthe engine cylinder. During the period that the port apertures arealigned, incoming air (or air/fuel mixture) is inlet from an intakemanifold passage (not shown), or outgoing exhaust gas is outlet into anexhaust manifold passage (not shown).

RVP-3 (70) in FIG. 1C and RVP-9 (250) in FIG. 1I are variations oralternate embodiments of the top-side placement of the rotating port, inwhich the port is formed in a gear that rotates in a plane parallel withthe top side of the cylinder and over and above the fixed ports in thecylinder head or top side of the cylinder.

RVP-6 (160) in FIG. 1F and RVP-7 (190) in FIG. 1G are variations oralternate embodiments of the top-side placement of the rotating port, inwhich the port is formed in a cylindrical extension of the rotating gearand positioned over and above the fixed ports in the cylinder head ortop side of the cylinder.

RVP-4 (100) in FIG. 1D and RVP-10 (280) in FIG. 1J are variations oralternate embodiments of the side-placement of the rotating port, inwhich the port is formed in a downward-disposed cylindrical extension ofa rotating gear whose axis of rotation is along a centerline of theengine cylinder. These two embodiments differ in the combination ofdriven gears coupling the rotating gear to the crankshaft. RVP-4 (100)in FIG. 1D employs a single drive gear; RVP-10 (280) in FIG. 1J employsfirst and second small drive gears disposed on opposite ends of anintermediate cylindrical coupling tube.

RVP-5 (130) in FIG. 1E and RVP-8 (220) in FIG. 1D are variations oralternate embodiments of the side-placement of the rotating port inwhich the rotating port is formed in the wall of a cylinder that rotateson an axis coincident (RVP-5) in FIG. 1E or parallel (RVP-8) in FIG. 1Hwith the axis of the engine cylinder and periodically positions therotating port in alignment with the fixed port in the side wall of theengine cylinder. RVP-5 (130) places the rotating cylinder alongside theengine cylinder on an axis of rotation separate from the enginecylinder. RVP-8 (220) places the rotating cylinder around the enginecylinder such that its axis of rotation is shared with—i.e., coincidentwith—the axis of the engine cylinder.

Of the ten configurations depicted in FIG. 1, two examples of aside-placement of the rotating valve port will be described in FIGS. 2and 5; similarly, two species of a top-side placement of the rotatingvalve port will be described in FIGS. 3 and 4. All of the examples usesimilar concepts and components in structure and operation. Each of thecomponents is identified by a reference number and bears the samereference number if shown in more than one figure. However, FIGS. 2, 3,4, and 5 omit the engine cylinder in the isometric views for clarity.Reference to FIG. 6, which depicts the engine cylinder 310 and acylinder head 330 in cross section, illustrates the relationship of thecylinder valve ports 322 (intake) and 326 (exhaust) in the enginecylinder 310.

FIG. 2 illustrates an isometric view of a first embodiment RVP-1 (10) ofthe present invention, an example of an engine assembly 10 having aside-placement of the rotating valve port concept. The engine assembly10 includes in outline an engine block 11, a crankcase 12, and acrankshaft 13 supported in the junction of the engine block 11 andcrankcase 12. A piston 15 is coupled to the crankshaft 13 by aconnecting rod 14 for reciprocating motion within the engine cylinder310 (Sec FIG. 6). On a first side of the assembly 10 is a rotating gear16 that meshes with a drive gear 17 on the crankshaft 13 such that therotating gear 16 rotates next to the first side of the engine cylinder310. In the rotating gear 16 an intake port 20 is formed through thebody of the rotating gear 16, and the rotating gear 16 rotates about anaxis on a center 22. Similarly, on a second side of the assembly 10 is arotating gear 18 that meshes with a drive gear 19 on the crankshaft 13such that the rotating gear 18 rotates next to the second side of theengine cylinder 310. In the rotating gear 18 an exhaust port 21 (notvisible in this view, but see, e.g., FIG. 6) is formed through the bodyof the rotating gear 18, and the rotating gear 18 rotates about an axison a center 23.

Continuing with FIG. 2, a multi-stage throttle valve 24 (“MS valve”) isshown withdrawn from a passage 25. The MS valve may be positionedbetween the rotating intake valve port 20 and the fixed intake valveport in the wall of the engine cylinder 310 (See FIG. 6) and configuredto vary the cross sectional area of the passage through the intake intothe engine cylinder 310. Operation of the valve 24 will be described inFIG. 8. An aperture 28 may be threaded and provided for a spark plug 30or other energetic ignition component such as a laser igniter. Anotheraperture 29 may be threaded and provided for a fuel injector 31 whendirect fuel injection is provided, which is preferred in the illustratedembodiment. As well-known in the art, the fuel may be introduced orinjected into a port or manifold passage to be mixed with the incomingair before it is admitted through an intake port into the enginecylinder. Another example of the latter would be a throttle-bodyinjection structure, where both a throttle valve and a fuel injector aredisposed along an intake port of a manifold, in the manner of aconventional carburetor.

FIG. 3 illustrates an isometric view of a second embodiment RVP-2 of thepresent invention, an example of a top-side placement of the rotatingvalve port concept. The engine assembly 40 includes in outline an engineblock 41, a crankcase 42, and a crankshaft 43 supported in the junctionof the engine block 41 and crankcase 42. A piston 45 is coupled to thecrankshaft 43 by a connecting rod 44 for reciprocating motion within theengine cylinder 310 (See FIG. 6). On a first side of the assembly 40 isa rotating gear 46 that meshes with a drive gear 47 on the crankshaft 43such that the rotating gear 46 rotates next to the first side of theengine cylinder 310. On the rotating gear 46 an intake port 50 is formedin a cylindrical ring—a short cylindrical extension 52 of the rotatinggear 46, and the rotating gear 46 rotates about an axis on a center 54.Similarly, on a second side of the assembly 40 is a rotating gear 48that meshes with a drive gear 49 on the crankshaft 43 such that therotating gear 48 rotates next to the second side of the engine cylinder310. In the rotating gear 48 an exhaust port 51 is formed in a shortcylindrical extension 53 of the rotating gear 48, and the rotating gear48 rotates about an axis on a center 55.

Continuing with FIG. 3, a multi-stage throttle valve 56 is shownwithdrawn from a passage 57. The valve 56 may be positioned between therotating intake valve port 50 and the fixed intake valve port (See FIG.6) in wall of the engine cylinder 310 and configured to vary the crosssectional area of the passage through the intake into the enginecylinder 310. Operation of the valve 56 will be described in FIG. 8. Anaperture 58 may be threaded and provided for a spark plug 60 or otherenergetic ignition device. Another aperture 59 may be threaded andprovided for a fuel injector 61.

FIG. 4 illustrates an isometric view of a third embodiment RVP-6 of thepresent invention, in a second example of a top-side placement of therotating valve port concept. It is drawn with a perspective to depictthe rotating valves more clearly by locating the respective gears on theback side of the view in FIG. 4. The engine assembly 160 includes inoutline an engine block 161, a crankcase 162, and a crankshaft 163supported in the junction of the engine block 161 and crankcase 162. Apiston 165 is coupled to the crankshaft 163 by a connecting rod 164 forreciprocating motion within the engine cylinder 310 (See FIG. 6).

Continuing with FIG. 4, on a first side of the assembly 160 is arotating gear 166 that is coupled through idler gears 167B and 167A to adrive gear 167 disposed on the crankshaft 163 such that the rotatinggear 166 causes the cylindrical extension 170 attached to the rotatinggear 166 along their common axis to rotate and position the rotatingport aperture 171 formed in the cylindrical extension 170 to align withthe fixed port in the top side of the engine cylinder 310. Similarly, asecond rotating gear 168 may also be coupled through the idler gears167B and 167A to the drive gear 1167 disposed on the crankshaft 163 suchthat the rotating gear 168 causes its cylindrical extension 172 attachedto the rotating gear 168 along their common axis to rotate and positionthe rotating port aperture 173 formed in the cylindrical extension 172to align with the fixed port in the top side of the engine cylinder 310.The multi-stage valve 174 shown in this view reciprocates in themulti-stage valve port 175 similar to the multi-stage valves shown inFIG. 3. An aperture 178 may be threaded and provided for a laser igniteror spark plug 180, Another aperture 179 may be threaded and provided fora fuel injector 181.

A word about implementation of RVP-6 and RVP-7, shown m FIG. 1 with asecond lower (intermediate) idler gear and a first upper (intermediate)idler gear 167A for transferring the rotation of the crankshaft to therotating valve gears 166 and 168. Two idler gears are shown as onepreferred configuration that avoids more difficult space considerationslikely if a single idler gear is used. Another issue is the gear ratiosnecessary to synchronize the valve operations with the four cycle or twocycle timing sequences. It will also be noted that the second rotatingvalve gear 168 may be offset from the plane of the first rotating valvegear 166 to permit them being driven by the same drive-and-idler gearconfiguration. These and other related issues will be discussed furtherduring the description of FIG. 12.

FIG. 5 illustrates an isometric view of a fourth embodiment RVP-8 of thepresent invention, in a second example of a side-placement of therotating valve port concept. FIG. 5, the isometric view, will bedescribed with reference to FIG. 6, a side cross section view, in thefollowing description. The engine assembly 220 includes in outline anengine block 221, a crankcase 222, and a crankshaft 223 supported in thejunction of the engine block 221 and crankcase 222. A piston 225 iscoupled to the crankshaft 223 by a connecting rod 224 for reciprocatingmotion within an engine cylinder. An engine cylinder is not shown inFIG. 5 for clarity of these engine structures. However, reference toFIG. 6 depicts a side cross section view of an engine cylinder 310 thatis typical of the Type A side-placement embodiments defined previously,which includes a second port 322 (Bar the intake side) and a second port326 (for an exhaust side) disposed through the wall of the enginecylinder 310.

Continuing with FIG. 5, a first side of the assembly 220 is a rotatinggear 226 that meshes with a drive gear 227 on the crankshaft 223 suchthat the rotating gear 226 causes the cylindrical extension 242 attachedto the rotating gear 226 along their common axis to rotate and positionthe rotating port aperture 230 (see also the rotating port 320 in FIG.6) formed in the cylindrical extension 242 to align with an intake portsuch as the intake port 322 disposed in the wall of the engine cylinder310 as shown in FIG. 6. The intake port 322 may be disposed in the upperportion of the engine cylinder 310 leading directly into the combustionchamber 336 above the piston 225 of FIG. 5 (or the piston 308 in FIG.6). Similarly, a second rotating gear 228 may also be coupled to thedrive gear 229 disposed on the crankshaft 223 such that the secondrotating gear 228 causes its cylindrical extension 243 attached to thesecond rotating gear 228 along their common axis to rotate to cause therotating port aperture 231 formed in the cylindrical extension 243 toalign with an exhaust port in the wall of the engine cylinder as is theexhaust port 326 in the engine cylinder 310 of FIG. 6. The exhaust port326 may be disposed in the upper portion of the engine cylinder 310leading directly out of the combustion chamber 336.

The inlet and outlet passages for the inlet air/fuel mixture and theexhaust waste gases (not shown in FIG. 5) may be disposed to enterthrough one side of the respective valve cylinder for coupling with therespective valve port inside the valve cylinder. The valve timing may beset by the number of teeth on the gears, with the valve cylinderextensions rotating at one-half the crankshaft speed in a four cycleengine. The valve cylinder extensions as depicted in the Figures may besupported in cylindrical bearing surfaces whose diameter is slightlygreater than the diameter of the valve cylinders. The valve cylindersmay be lubricated by a connection (not shown) with the pressurizedlubrication system of the engine in a manner similar to the lubricationof the crankshaft journal bearings that support the crankshaft in thecrankcase. The axial length of the valve cylinders may be varieddepending on the size of the valve port opening, the space available inthe engine block, the position of the second (fixed port in the wall ofthe engine cylinder, etc. However, to minimize friction and the loadingon the rotating element, the axial length may generally be less thanshown in FIG. 4 or 5.

FIG. 6 illustrates a schematic cross section of a conceptual embodimentof a single cylinder internal combustion engine 300 having rotatingvalve ports according to the present invention. A representation of anengine block 302 includes a crankshaft 304, and a connecting rod 306connected to the lower end of a piston 308 for imparting reciprocatingmotion within a cylinder 310. Included next to the walls of the cylinder310 is a first rotating valve gear 312 driven by a first drive gear 314on the crankshaft 304. Similarly, a second rotating valve gear 316 isdriven by a second drive gear 318 also connected to the crankshaft 304.The rotating valve gear 312 includes an intake valve port 320 alignedwith an intake port 322 in the upper portion of the wall of the cylinder310 just below the cylinder head 330. The rotating valve gear 316includes an exhaust valve port 324 aligned with an exhaust port 326 inthe upper portion of the wall of the cylinder 310 just below thecylinder head 330. An energetic ignition component such as a laserigniter (not shown) or spark plug 332 for igniting the air/fuel mixtureis disposed in the top side of the cylinder head 330 and extending intoa combustion chamber 336.

Continuing with FIG. 6, the first rotating valve port 312 may rotate onan axle stub or shoulder bolt 338 set through a bushing 340 into atapped hole 342 in the wall of the engine cylinder 310. Similarly, thesecond rotating valve port 316 rotates on an axle stub or shoulder bolt344 set through a hushing 346 into a tapped hole 348 in the wall of theengine cylinder 310. The axes of rotation of the rotating valve ports312, 316 are defined respectively by the shoulder bolts 338 and 344.

Sealing the rotating valve port structure to contain leakage of intakeor exhaust mixtures or gases may be developed from several alternatives.As is well-known, sealing the space between an engine cylinder and apiston is provided by piston rings, usually one for controlling thedispersion of lubricating oil and one or two others for preventingcombustion gases from entering the crankcase and maintaining thepressure within the cylinder during the two or four cycles of the ICEoperation. Other alternatives include gaskets and O-rings.

FIG. 7 illustrates a side view of an engine cylinder 310 as formed inthe embodiment of FIG. 2. An intake side face 352, and the exhaust sideface 354 are machined flat on opposite sides of the wall of the enginecylinder 310 to provide a smooth surface to receive a sealing mechanismformed by an inner gasket 356 and an outer compression ring 358, whichare disposed between the side of the engine wall around the intake port322 and the exhaust pert 326 respectively. In an alternate embodimentthe compression ring 358 may be replaced by a sealing ring by applying aheat-resistant synthetic compound or gasket in the groove formerlyoccupied by the compression ring 358. The groove for a sealing ring maybe machined in the face of the rotating valve disc or the wall of theengine cylinder 310 to provide the sealing structure shown in FIG. 7. Insome embodiments the gasket may be an O-ting specifically shaped to fitthe machined groove.

In another alternate embodiment, the effectiveness of the seal may beenhanced by coating the facing surfaces of the wall of the enginecylinder 310 and the rotating member embodying the rotating valve portwith a high-temperature ceramic material such as a ceramic paint, apowder coating with embedded ceramic material that can beelectrostatically applied, or a powder coating alone. The coating mayalso be applied to the Multi-Stage valve structure to be described inFIGS. 8A through 10. These ceramic or powder coating materials mayprovide a surface finish that is more resistant to wear, therebyreducing the heat build-up through reduced friction between the rotatingvalve port member and the side wall of the engine cylinder.

Other methods or structures for seating the RVP mechanisms may includemachined ridges and/or grooves in the surfaces of the wall of the enginecylinder or the face of the rotating valve. For example, the inside faceof the rotating valve disc may be equipped with two concentriccylindrical extensions or rings, radially-disposed on either side of thevalve port formed in the rotating valve disc. The seal may be completedby forming corresponding grooves in the wall of the engine cylinder toreceive the cylindrical extensions (rings). Another example using thisridge-and-groove concept is illustrated in FIG. 15. In FIG. 15, the wallof the engine cylinder around the border of the second valve port may bemachined to include a small ridge no larger than about 0.040″ above thesurface of the wall of the engine cylinder; and the face of the rotatingvalve disc may be inset by the same 0.040″ depth between radii thatstraddles the radial dimensions of the first valve port in the rotatingdisc. When assembled, any leakage is contained within the space betweenthe wall of the engine cylinder and the inset face of the rotating discand bounded by the outer and inner sides of the inset space. Thisexample may be identified as the combination of a ridge around the(fixed) second port and a facial inset around the first (rotating) valveport. It is an example that reduces the required machining to a minimumby including it during the manufacture of the engine cylinder and therotating valve disc themselves.

In one variation of the structure depicted in FIG. 15, the inset regionmay be formed in the inner face of the rotating, valve disc and theridge or elevated feature formed in the outer face of the wall of theengine cylinder.

FIG. 8 illustrates four views, FIGS. 8A, 8B, 8C, and 8D, of amulti-stage valve system 360 for use in the embodiment of FIG. 2. Eachdiagram includes a rotating valve gear 16 and a respective valve port20. The multi-stage valve (“MSV”) system, which is used to vary thecross sectional area of the rotating valve ports 320, 324, provides away to regulate operation of the RVP engine. The MSV (or MS valve) maybe used as a throttle when disposed as part of the rotating intake valveapparatus of the engine. It may also be used to regulate the crosssectional area of the exhaust valve port, not as a throttle valve butfor purposes associated with the temperatures of the combustion chamber336 and the exhaust gases, the emission levels of the engine exhaust,etc. These parameters may be controlled through an appropriatemechanical linkage by computer control that may be configured bysoftware, for example, FIGS. 8A-8D depict four views or states of oneembodiment of the multi-stage valve used as a throttle controlled byengine vacuum. As will be described, the MS valve may be configured as athin baffle attached to a vacuum diaphragm link so that it may bereciprocated toward and away from alignment with the intake valve port,thus providing a mechanism to vary the cross sectional area of theintake valve port into the cylinder thereby to act as a throttle valve.

Continuing with FIG. 8A, a vacuum diaphragm assembly 362 includes ahousing 364, a vacuum diaphragm 366, a return spring 368, and anoperating rod 370 connected at one end to the vacuum diaphragm 366 andthe return spring 368, both located within the housing 364. The oppositeend of the operating rod 370 is connected to an MSV plate 374. A vacuumport 372 connects the interior of the vacuum diaphragm 366 to a sourceof vacuum 380 regulated by a throttle or “accelerator” (not shown) ifthe vacuum diaphragm assembly 360 is used to control the volume of airfuel mixture admitted into the combustion chamber 336 via the rotatingintake valve 312. The MSV plate 374 includes a valve port 376 that maybe aligned with the rotating valve port 20. Motion of the MSV plate 374can be varied from fully withdrawn as in FIG. 8A when the engine is notoperating, engine vacuum is zero and the spring 368 is fully expanded,to fully-advanced as in FIG. 8D corresponding to wide open throttle whenthe engine vacuum is at it's minimum level and the spring 368 is nearlyfully expanded. FIG. 8B depicts the approximate position of the MSVplate 374 provided by the maximum vacuum condition that occurs when theengine is idling. FIG. 8C depicts the approximate position of the MSVplate 374 provided at a part-throttle condition such as when the vehicleor machine is operating under a moderate load. Control of the MS valvemay be assisted in its advance by the return spring 368 that suppliesthe force to advance the MS valve, in opposition to the force applied tothe vacuum diaphragm, which acts to retract the MS valve. The MS valvethus can be operated as a throttle valve to vary the engine's poweroutput.

FIG. 9 illustrates a top-down view of a cross section of an enginecylinder 310 according to the embodiment of FIG. 2 that includes an MSintake valve 374 depicted in FIG. 8A in a closed-throttle state. Therepresentation of an engine block 302 includes the engine cylinder 310and its associated intake 322 and exhaust 326 ports formed in the wallsof the engine cylinder 310. The rotating valve gear 312 is shownadjacent the engine cylinder 310. Similarly, a rotating valve gear 316is shown adjacent the exhaust valve port 326. Also shown FIG. 9 areedge-wise views of the location of first (intake) 402 and second(exhaust) 404 seals disposed between the adjacent wall of the enginecylinder 310 and the rotating valve gear. The seal structure isdescribed briefly in FIG. 7. Disposed next to the engine block 302 isone embodiment of as vacuum diaphragm assembly 362 supported by abracket 406.

FIG. 10 illustrates a top-down view of a cross section of an enginecylinder according to the embodiment of FIG. 2 that includes an MSintake valve depicted in FIG. 8D in a wide-open throttle state. As inFIG. 9, the representation of an engine block 302 includes the enginecylinder 310 and its associated intake 322 and exhaust 326 ports formedin the walls of the engine cylinder 310. The rotating valve gear 312 isshown adjacent the engine cylinder 310. Similarly, a rotating valve gear316 is shown adjacent the exhaust valve port 326. Also shown in FIG. 9are edge-wise views of the location of first (intake) 402 and second(exhaust) 404 seals disposed between the adjacent wall of the enginecylinder 310 and the rotating valve gear. The seal structure isdescribed briefly in FIG. 7. Disposed next to the engine block 302 isone embodiment of a vacuum diaphragm assembly 362 supported by a bracket406.

FIG. 11 illustrates a simplified isometric view of a lower portion ofthe cylinder head assembly formed of a cylinder head 436 and a cylinderhead cover 438 of the embodiment of FIG. 4 depicting first 434 andsecond 444 cylindrical extensions, respectively of rotating valve gears454 and 464 (not shown in FIG. 11 but see FIG. 12). The cylinder headcover 438 is shown in phantom. The illustrated rotating cylindricalextension 434 includes a port aperture 442 formed through the wall ofthe cylindrical extension 434; similarly, cylindrical extension 444includes a port aperture 446 formed through the wall of the cylindricalextension 444. Each cylindrical extension 434, 444 rotates on arespective bearing surface 428, 448 that are formed in the cylinder head436. A spark plug 432 or other energetic component such as a laserigniter may be fitted into a threaded hole in the cylinder head 436.Similarly, provision may be made for a fuel injector for directinjection of fuel into the combustion chamber as discussed in FIGS. 2and 4.

The inlet and outlet passages for the inlet air/fuel mixture and theexhaust waste gases (not shown) may be disposed through one side (orend, in the elongated valve cylinders) of the respective valve cylinderto contact with the respective valve port inside the valve cylinder. Thevalve timing may be set by the number of teeth on the gears, with thevalve cylinders rotating at one-half the crankshaft speed. The valvecylinders may be supported in cylindrical bearing surfaces whosediameter is slightly greater than the diameter of the valve cylinders.The valve cylinders may be lubricated by a connection (not shown) withthe pressurized lubrication system of the engine in a manner similar tothe lubrication of the crankshaft journal bearings that support thecrankshaft in the crankcase. The axial length of the valve cylinders maybe varied depending on the size of the valve port opening and the spaceavailable in the engine block. However, to minimize friction, the axiallength may generally be less than shown in FIG. 4 or 5.

FIG. 12 illustrates a timing gear set 450 for use with the embodiment ofFIG. 11. The intake rotating valve or drive gear 454 is attached to thecylindrical extension 434 along and axis common to the rotating valvegear 454 and the cylindrical extension 434. Similarly, the exhaustrotating valve or drive gear 464 is attached to the cylindricalextension 444 along and axis common to the rotating valve gear 464 andthe cylindrical extension 444. The rotating drive gears 454, 464 may bedisposed to mesh with an intermediate or idler gear 456, which is inturn disposed to mesh with a crankshaft gear 458. In the illustratedexample, the driven rotating valve gears 454, 464 have the same numberof teeth around the perimeter to preserve the 2:1 timing relationshiprelative to the intermediate or idler gear 456, which also has twice thenumber of teeth around its perimeter as the crankshaft drive gear 458,so that the 2:1 timing relationship of crankshaft rotation and rotatingvalve port are maintained.

FIG. 13A through 13J illustrate cross section drawings that eachcorrespond by reference number to each of the members of the family ofembodiments depicted in FIGS. 1A through 1J. As in the series ofisometric views of FIGS. 1A through 1J, RVP 1 is identified by referencenumber 10; RVP 2 by reference number 40; etc. through RVP 10 identifiedby reference number 280 in FIGS. 13A through 13J.

FIGS. 14A and 14B illustrate a method for timing the operation of intakeand exhaust valves of an internal combustion engine according to thepresent invention. This embodiment is directed to one of the three kindsof timing functions that must be satisfied in an internal combustionengine and depicted in the flow chart of FIGS. 14A and 14B. In aninternal combustion engine having a crankshaft rotatably mounted in acrankcase portion of an engine block, an engine cylinder formed withinthe engine block and open at a lower end thereof into the crankcase, anda combustion chamber formed in an upper end of the engine cylinder, themethod may comprise the steps of forming a first valve port in a sidewall of the engine cylinder proximate the combustion chamber; forming avalve port mechanism having a second valve port in a rotating memberdisposed against the side wall of the engine cylinder; and causing therotating member to rotate in synchronism with the crankshaft such thatthe second valve port periodically aligns with the first valve port topermit passage of intake or exhaust substances. In another aspect, themethod may include the steps of forming first and second valve portmechanisms for the intake and exhaust substances, and disposing therespective first and second valve port mechanisms or combinations onrespective first and second opposite sides of the engine cylinder topermit passage of both intake and exhaust substances. A further step mayinclude coupling inlet and outlet passages of a manifold with therespective first and second port valve port mechanisms, respectively forconveying inlet air and outlet exhaust substances.

Accordingly, in one embodiment, the method 500 illustrated in FIGS. 14Aand 14B proceeds from the Start 502 point in FIG. 14A as follows, toconfigure for each cylinder of an internal combustion engine having acrankcase supported in an engine block having an engine cylinder formedtherein and open at a lower end thereof into a crankcase, and acombustion chamber formed in an upper end of the cylinder as noted instep 504. The flow advances to step 506 to locate a first port near anupper end of the engine cylinder near the combustion chamber, followedby step 508 to form the first port trough the side wall of the enginecylinder, shaped to correspond to alignment with a second port in motionpast the first port. In step 510, the process locates the second portalong a radial portion of a rotating disc configured as a ring gear, thesecond port shaped to correspond with to the first port as the secondport passes the first port. The process continues in step 512 whereinthe rotating member containing the second port is supported on a bearingdisposed adjacent the side wall of the engine cylinder such that thefirst and second ports automatically align periodically.

Continuing with FIG. 14A, in step 514, one first and second portcombination is designated for an engine intake port and another firstand second port combination is designated as an engine exhaust port.Thus, the rotating valve port concept may be employed for both an engineintake port and an engine exhaust port. In the following step 516 theremay be provided a first manifold passage for an air/fuel mixture coupledto the engine intake port and a second manifold passage provided for anexhaust gas coupled from the engine exhaust port. Proceeding to FIG.14B, Step 518 of the process functions to synchronize the rotation ofthe second port to pass the first port when an air/fuel mixture or anexhaust gas must be respectively inlet to or outlet from the enginecylinder. A related part of step 518 includes adapting in step 520 thesynchronization for a four cycle engine or a two cycle engine. If thesynchronization is for a four cycle engine the process advances to step522 to configure the gear ratio of the rotating member to the crankshaftat a 1 to 2 ratio, followed by step 526 to control the fuel and ignitiontiming for four cycle operation of the engine. Similarly, if thesynchronization is for a two cycle engine the process advances to step524 to configure the gear ratio of the rotating member to the crankshaftat a 1 to 1 ratio, allowed by step 528 to control the fuel and ignitiontiming for four cycle operation of the engine. Thereafter, the processends at step 530.

FIG. 15 depicts one embodiment of a sealing structure 540 that confinesleakage gases to the immediate region around the joint in the portpassages between the rotating, and fixed portions of the port structure.The engine block 550 includes an engine cylinder 552 and a second fixedport 554 formed in an inset region 560 of the face 564 of the engineblock 550. The face 564 in this example is coincident with and may alsobe called the outer wall of the engine cylinder 552. The inset region560 may be defined by a low elevation ridge 562 formed between an axle572 and a position just beyond the location of the fixed second valveport 554. The low elevation ridge may have an elevation for examplebetween approximately 0.010″ and 0.060″ above the surface of the insetregion 560.

Similarly, the face 566 of the rotating valve disc 556 may include alow-elevation raised region 568 formed to the same 0.010″ to 0.060″dimension between the hub 574 and a ridge 570 formed at a radius justshort of the inner-most radial dimensions of the first valve port in therotating valve disc 556.

When assembled, any leakage is contained within the space between theinset region 560 of the face 564 of the engine block 550 and the innerface 566 of the rotating valve disc 556 and bounded by the outer 560 andinner 570 edges of the inset region 560. This example may be identifiedas the combination of the ridge 562 around the (fixed) second port andthe ridge 570 around the hub 574 of the rotating first valve port 558.

The embodiment illustrated in FIG. 15 is one example that reduces therequired machining to a minimum by including it as part of themanufacture of the engine cylinder block 550 and the rotating valve disc556. Thus, in one variation of the structure depicted in FIG. 15, theinset region may be formed in the outer face 564 of the wall of theengine cylinder block 550 and the inner face 566 of the rotating valvedisc 556, such that the sealing apparatus comprises a circular ridge 570formed on an inner face of the rotating valve disc 556 between a centralhub 574 and the first port 558; and a circular inset region 560 disposedin an outer face 564 of the wall of the engine cylinder block 550between the axle 572 and extending to the ridge 562 disposed at a radiusjust beyond the fixed second port 554.

In one variation of the structure depicted in FIG. 15, the inset regionmay be formed in the inner face 566 of the rotating valve disc 556 andthe ridge or elevated feature formed in the outer face 564 of the wallof the engine cylinder block 550. Thus, the sealing apparatus maycomprise a circular inset region disposed in an inner face of therotating valve disc between the central hub 574 and extending to aradius just beyond the rotating first port 558; and a circular ridgeformed on an outer face 564 of the wall of the engine cylinder block 550between the axle 572 and the fixed second port 554.

The disclosed invention described therein eliminates the conventionalcamshaft and reciprocating valve train to control the timing of theintake and exhaust cycles of an internal combustion engine (“ICE”) suchas the well-known two or four cycle, spark ignition engines. The systemincludes intake and exhaust port valves for admitting the air/fuelmixture into the cylinder and exhausting the burned gases of combustionfrom the cylinder. It is important to note that the valve structure ofthe present invention ensures free and direct low through both theintake and exhaust valves when the valves are fully open, withoutobstruction to such flow by the open valve as in conventional poppetvalve trains. The valve ports are located adjacent the engine cylinderand the timing of the valve operation is operated directly from thecrankshaft, without any intervening valve train mechanism, therebyreducing the number of moving parts to a minimum. A camshaft is notneeded, nor are lifters, pushrods, valve springs, valves with keepersand retaining washers, and features provided for adjusting valveclearances, nor any of the supporting structure required to support thecomponents of a valve train, etc. Valve timing upon assembly is assimple as lining up two marks on the valve gear drive.

While the invention has been shown and described in only one of itsforms, it is not thus limited but is susceptible to various changes andmodifications without departing from the spirit thereof. For example,the rotating member containing the valve port (intake or exhaust) hasbeen described in several examples as a valve gear even though otherembodiments may employ a rotating disc that is configured with adifferent means of coupling it to the crankshaft rotation to preservethe necessary timing relationship between the crankshaft and the openingand closing of the valves.

In another example, a cylinder head may be configured with curved,tubular ports into the combustion chamber, wherein the respective inletor outlet opening (of the intake or exhaust port) positioned just abovethe respective outer side of the cylinder and in the same plane as theadjoining valve port in the rotating disc. This would route the portsinto the top of the cylinder instead of through the side wall of thecylinder, thereby simplifying the configuration of the cylinder portionof the engine block.

In yet another embodiment not depicted in the included drawings, thevalve disc, instead of being formed as a ring gear, may be a rotatingvalve disc driven by a small gear attached to one face of the rotatingvalve disc and aligned on the axis of rotation of the valve disc,wherein the small gear is driven at one-half crankshaft speed by anintervening gear mechanism coupled to the crankshaft. Such an embodimentmay reduce weight and wear due to the lower mass of the valve disc andthe structure needed to rotate it at the required speed.

What is claimed is:
 1. An internal combustion engine valve systemcomprising: (a) engine block (161); (b) engine cylinder head (436); (c)crankcase (162); (d) crankshaft (163); (e) connecting rod (164); (f)piston (165); (g) first rotating gear (166); (h) first idler gear(167B); (i) second idler gear (167A); (j) drive gear (167); (k) firstcylindrical extension (170); (l) multi-stage valve (174); (m)multi-stage valve port (175); wherein: said engine block (161) comprisesan engine cylinder (310); said engine cylinder (310) conforms to acircumferential shape of said piston (165) and comprises a top sectioncomprising a combustion chamber; said combustion chamber is formed bywalls of said engine cylinder (310) in said engine block (161) and saidcylinder head (436); said crankshaft (163) is supported in the junctionof the engine block (161) and crankcase (162); said piston (165) iscoupled to the crankshaft (163) by said connecting rod (164) forreciprocating motion within said engine cylinder (310); said firstcylindrical extension (170) is positioned at a top-side placement ofsaid engine cylinder (310); said first rotating gear (166) is coupledthrough said first idler gear (167B) and said second idler gear (167A)to said drive gear (167); said drive gear (167) is disposed on saidcrankshaft (163); said first cylindrical extension (170) comprises afirst tube; said first tube comprises a first distal end, a seconddistal end, a first hollow center, and a first circumferential surface;said first circumferential surface comprises a first rotating portaperture (171) open to said first hollow center; said first distal endis mechanically coupled to said first rotating gear (166) along an axiscommon to said first rotating gear (166) and said first cylindricalextension (170); said second distal end comprises a first open end(182); said first rotating gear (166) causes said first cylindricalextension (170) attached to said first rotating gear (166) along theircommon axis to rotate and position said first rotating port aperture(171) formed in the first cylindrical extension (170) to align with afirst fixed port in the top side of said engine cylinder (310); saidengine block (161) further comprises the multi-stage valve port (175)open to said engine cylinder (310); said multi-stage valve (174) ispositioned between said first rotating port aperture (171) and saidmulti-stage valve port (175); said multi-stage valve (174) reciprocatesin said multi-stage valve port (175); and said multi-stage valve (174)is configured to vary the cross sectional area of the passage betweensaid first rotating port aperture (171) and said multi-stage valve port(175) into the engine cylinder (310).
 2. The internal combustion enginevalve system of claim 1 wherein said first idler gear (167B) and saidsecond idler gear (167A) are replaced by a single idler gear.
 3. Theinternal combustion engine valve system of claim 1 wherein said firstidler gear (167B) and said second idler gear (167A) are configured tohave gear ratios corresponding to synchronized timing for a 2-cycleinternal combustion engine based on the relative position of said piston(165) and said first rotating port aperture (171).
 4. The internalcombustion engine valve system of claim 1 wherein said first idler gear(167B) and said second idler gear (167A) are configured to have gearratios corresponding to synchronized timing for a 4-cycle internalcombustion engine based on the relative position of said piston (165)and said first rotating port aperture (171).
 5. The internal combustionengine valve system of claim 1 wherein a drivetrain comprising saidfirst rotating gear (166), said first idler gear (167B), said secondidler gear (167A), and said drive gear (167) are configured to maintaina 2:1 timing relationship of rotation of said crankshaft (163) and saidfirst cylindrical extension (170).
 6. The internal combustion enginevalve system of claim 1 wherein said engine block (161) furthercomprises at the top of said engine cylinder (310) a threaded aperture(178) configured for mechanically coupling a laser igniter or spark plug(180) to said engine block (161).
 7. The internal combustion enginevalve system of claim 1 wherein said engine block (161) furthercomprises at the top of said engine cylinder (310) a threaded aperture(179) configured for mechanically coupling a fuel injector (181) to saidengine block (161).
 8. The internal combustion engine valve system ofclaim 1 wherein said system further comprises: (a) second rotating gear(168); (a) second cylindrical extension (172); wherein: said secondcylindrical extension (172) is positioned at a top-side placement ofsaid engine cylinder (310); said second rotating gear (166) is coupledthrough said first idler gear (167B) and said second idler gear (167A)to said drive gear (167); said second cylindrical extension (172)comprises a second tube; said second tube comprises a third distal end,a fourth distal end, a second hollow center, and a secondcircumferential surface; said second circumferential surface comprises asecond rotating port aperture (173) open to said second hollow center;said third distal end is mechanically coupled to said second rotatinggear (168) along an axis common to said second rotating gear (168) andsaid second cylindrical extension (172); said fourth distal endcomprises a second open end (183); and said second rotating gear (168)causes said second cylindrical extension (172) attached to said secondrotating gear (168) along their common axis to rotate and position saidsecond rotating port aperture (173) formed in the second cylindricalextension (172) to align with a second fixed port in the top side ofsaid engine cylinder (310).
 9. The internal combustion engine valvesystem of claim 8 wherein said second rotating valve gear (168) isoffset from the plane of said first rotating valve gear (166) to permitsaid second rotating valve gear (168) and said first rotating valve gear(166) being driven by the same drive-and-idler gear configuration. 10.The internal combustion engine valve system of claim 1 wherein saidfirst cylindrical extension (170) and said second cylindrical extension(172) each rotate on a respective bearing surface that are individuallyformed in said cylinder head (436).